Heat exchanger

ABSTRACT

The invention relates to a heat exchanger, in particular for use in a motor vehicle, in addition to a circuit comprising a heat exchanger.

The invention relates to a heat exchanger, in particular for use in amotor vehicle, and to a circuit with a heat exchanger.

Heat exchangers are often used in a motor vehicle, for example ascoolers, heating elements, condensers or evaporators. A modern vehiclehas a multiplicity of various heat exchangers which are designed, forexample, as coolers and cool different vehicle assemblies, vehiclecomponents or media in vehicle assemblies or vehicle components. Forexample, a coolant cooler for cooling the engine, such as, for example,the internal combustion engine or electric motor, a transmission oilcooler, an exhaust gas cooler, a charge air cooler and a hydraulic oilcooler are provided for the most diverse possible applications in avehicle and/or for further coolers.

The arrangement of a large number of heat exchangers in the vehiclenecessitates an increased construction space requirement and repeatedlyleads to conflicts between the existing construction space and therespective arrangement of the heat exchangers. In this case, this mayresult in certain compromises in terms of the arrangement of theindividual heat exchangers which may possibly not be ideal forthermodynamic reasons. Also, an increased construction space requirementarises due to the individual arrangement of the respective heatexchangers, since, because of existing manufacturing tolerances, moreconstruction space has to be made available than is possibly necessary.

The object of the invention is to provide a heat exchanger which isimproved, as compared with the prior art.

This is achieved, according to the invention, in that a heat exchanger,in particular for motor vehicle cooling systems, is designed in such away that it is provided with at least one fluid inlet and at least twofluid outlets, and with an arrangement of fluid connections betweeninlet, collecting, deflecting and/or outlet chambers, the fluidconnections being subdivided into various regions, a first region offluid connections being arranged between at least one inlet and onefirst outlet, and a further region of fluid connections being arrangedbetween the first outlet and a second outlet.

It is particularly expedient if a further third outlet is arranged and afurther region of fluid connections is provided between the secondoutlet and the third outlet. It may, however, also be expedient if afurther nth outlet is arranged and a further region of fluid connectionsis provided between the n−1-th outlet and the nth outlet, n preferablybeing 3, 4, 5, 6, 7, 8, 9, 10 or greater than 10.

It is also advantageous if individual regions of fluid connections areconnected to other regions of fluid connections and/or to at least oneinlet and/or at least one outlet by means of inlet, collecting,deflecting and/or outlet chambers.

In this case, it is expedient if the inlet, collecting, deflectingand/or outlet chambers are arranged preferably in side boxes arrangedlaterally with respect to the fluid connections, the side boxes beingcapable of being subdivided into various chambers by means ofpartitions. In this case, it is advantageous if the partitions aredesigned as vertical, horizontal or l-shaped, z-shaped, c-shaped orT-shaped walls or as walls formed compositely from these.

In one exemplary embodiment, it is expedient if a deflection in depth,that is to say in a plane of the fluid connections, is present betweenat least one first region of fluid connections and one second region offluid connections.

In a further exemplary embodiment, it is expedient if a deflection inwidth, that is to say in a plane perpendicular to a plane of the fluidconnections, is present between at least one first region of fluidconnections and one second region of fluid connections.

In a further exemplary embodiment, it is expedient if a deflection indepth and in width, that is to say in a plane of the fluid connectionsand in a plane perpendicular to a plane of the fluid connections, ispresent between at least one first region of fluid connections and onesecond region of fluid connections.

It is likewise advantageous if two regions of fluid connections arerouted in countercurrent without an outlet between them.

Furthermore, it is expedient if ducts for a further medium or fluid areprovided between the fluid connections. In this case, it may beparticularly expedient if these ducts are formed by ribs between thefluid connections. The medium may advantageously be air. The medium mayadvantageously be a fluid or liquid medium.

It is expedient if the fluid connections are tubes, preferably such asflat tubes or round tubes or oval tubes. It is likewise expedient if thetubes have a plurality of fluid ducts which do not communicate with oneanother over the length of the tubes. Furthermore, it is expedient ifthe fluid connections or tubes have a plurality of fluid ducts whichcommunicate with one another over the length of the tubes. Furthermore,it may be expedient if the fluid connections or tubes are arranged in asingle row or in a plurality of rows next to one another for each planeof the fluid connections.

According to a further idea of the invention, a fluid circuit isprovided, with at least one heat exchanger having at least one inlet andat least two outlets and with at least two assemblies which can besupplied by the heat exchanger by means of fluid lines and have a fluidinlet and a fluid outlet, characterized in that a pump with an inlet andoutlet is arranged between one outlet of the at least one heat exchangerand one inlet of at least one assembly, and at least one outlet of afurther assembly can be connected to the inlet side of the pump. What isadvantageously achieved thereby is that the number of pumps used can bereduced and, at the same time, the fluid stream for cooling the furtherassemblies can also be used for cooling the main assembly, such as thevehicle engine. The efficiency of the cooling system is thus furtherincreased. As a result, for example, the overall system can have avaried design and, where appropriate, structural parts and costs aresaved or have smaller dimensioning.

What may be considered as assemblies of the vehicle are the engine, thetransmission, a turbocharger, an injection pump, electronics, an exhaustsystem, hydraulic systems or further assemblies as heat sources. Wheresuch heat sources are concerned, it is often necessary for heat to bedischarged to the surroundings for purposes of cooling and of thermalcontrol.

It is advantageous if the further assembly is connected with its inletto an outlet of the heat exchanger. It is also expedient if a pluralityof further assemblies are connected in series and have the fluid flowingthrough them. It is also advantageous if a plurality of furtherassemblies are connected in parallel and have the fluid flowing throughthem. It is particularly advantageous if the inlet of a further assemblyis connected to an outlet of the heat exchanger.

The invention will be explained in more detail below by means ofexemplary embodiments in the figures of which:

FIG. 1 shows a diagrammatic illustration of a heat exchanger,

FIG. 2 shows a diagrammatic illustration of a heat exchanger,

FIG. 3 shows a diagrammatic illustration of a heat exchanger,

FIG. 4 shows a diagrammatic illustration of a heat exchanger,

FIG. 5 shows a diagrammatic illustration of a heat exchanger,

FIG. 6 shows a diagrammatic illustration of a heat exchanger,

FIG. 7 shows a diagrammatic illustration of a heat exchanger,

FIG. 8 shows a diagrammatic illustration of a heat exchanger,

FIG. 9 shows a diagrammatic illustration of a heat exchanger,

FIG. 10 shows a diagrammatic illustration of a heat exchanger,

FIG. 11 shows a diagrammatic illustration of a heat exchanger,

FIG. 12 shows a diagrammatic illustration of a heat exchanger,

FIG. 13 shows a diagrammatic illustration of a heat exchanger,

FIG. 14 shows a diagrammatic illustration of a heat exchanger,

FIG. 15 shows a diagrammatic illustration of a heat exchanger,

FIG. 16 shows a diagrammatic illustration of a heat exchanger,

FIG. 17 shows a diagrammatic illustration of a heat exchanger,

FIG. 18 shows a diagrammatic illustration of a heat exchanger, and

FIG. 19 shows a diagrammatic illustration of a cooling circuit.

FIG. 1 shows a heat exchanger, such as, for example, a cooler, a heater,a condenser or an evaporator. The heat exchanger will be describedbelow, without any restriction in generality, in terms of its functionas a coolant cooler.

The heat exchanger 1 has a fluid inlet 2 and a fluid outlet 3, so that afluid can flow through the heat exchanger between the inlet and theoutlet. The inlet is connected to a collecting chamber 4 and the outletto a collecting chamber 5. The fluid flows from the inlet 2 into thefirst collecting chamber 4, an inlet-side collecting chamber. The fluidflows from the second collecting chamber 5, an outlet-side collectingchamber, into the outlet 3. In FIG. 1, the inlet-side collecting chamber4 or the outlet-side collecting chamber is formed by a box-shapedelement 6 or 7, such as, for example, a water box or fluid box, whichcan be connected to a wall, such as tube sheets, 8 or 9 and is designedto be outwardly fluidtight. The parts 6 and 8 on the inlet side and theparts 7 and 9 on the outlet side are connected to one another in such away that the fluid located inside essentially cannot emerge.

Provided between the collecting chambers 4 and 5 are fluid connections10, through which the fluid can flow from the one collecting chamber 4to the other collecting chamber.

The fluid connection 10 consists essentially of a multiplicity ofparallel tubes 11, through which the fluid can flow inside from one sideto the other side. These tubes may be flat tubes or round tubes or otherconnecting tubes. These tubes may also have, inside them, various flowducts which are formed separately from one another or which are also atleast partially connected to one another at least in places. The tubes11 are arranged in such a way that free spaces are provided as an airpassage between them. Ribs 13 are preferably arranged in at least someof these free spaces 12, in order to form flow ducts for the air passageaccording to the arrow 14 and to improve heat exchange between the airand fluid passing through. The surface on the cooling-air side isthereby increased as effectively as possible.

The heat exchanger has the feature that the two participating media, forexample the cooling air and the fluid, are led in cross current.

The tube sheets and water boxes or fluid box form chambers which, on theinlet side, serve for distributing the coolant stream or fluid stream tothe tubes and, on the outlet side, for combining the coolant stream outof the tubes. The connections 2, 3, such as, for example, connectionpieces on the chambers, make it possible to connect the heat exchangerto a fluid circuit, such as, for example, a coolant circuit.

FIG. 1 illustrates the cooler network in a form of constructionpreferably consisting of flat tubes and of corrugated ribs. The tubesmay have the following forms of construction: round tube type ofconstruction, oval tube type of construction or bundle type ofconstruction.

FIG. 2 shows a diagrammatically illustrated heat exchanger 101 accordingto the invention which operates on the basis of cross current routingand/or cross countercurrent routing. Cross current routing means thatthe one fluid stream and the second fluid stream intersect. Crosscountercurrent routing means that the one fluid stream and the secondfluid stream intersect, the second fluid stream in this case alsoexperiencing a deflection, so that both an outward and a returning fluidstream intersect with the first fluid stream, that is to say oppositefluid streams intersect with the other fluid stream.

The heat exchanger 101 has at least one first fluid inlet 102 and onefirst fluid outlet 103 and one second fluid outlet 103 a, so that afluid can flow through the heat exchanger 101 between the inlet 102 andthe first or the second outlet. The inlet 102 is connected to acollecting chamber 104 and the first outlet to a collecting chamber 104a and the outlet is connected to a further collecting chamber 105. Thefluid flows from the inlet 102 into the first collecting chamber 104, aninlet-side collecting chamber. The fluid flows from there through thefluid connections 110 into a further collecting chamber 104 b, anintermediate chamber. The fluid is deflected in the intermediate chamber104 b and is led through the fluid connections 110 a, counter to thedirection of flow in the fluid connections 110, to the collectingchamber 104 a. A first part of the fluid stream is branched off from thecollecting chamber 104 a through the one outlet 103 and is dischargedinto a fluid circuit. A further part of the fluid stream is led througha further part of the fluid connections 110 b to the collecting chamber105. The fluid emerges from the heat exchanger there and is supplied toa further fluid circuit or part circuit.

A design of the heat exchanger with a first stage, which is illustratedby the components 102, 104, 110, 104 b, 110 a, 104 a and 103, isadvantageous. This is a cross countercurrent heat exchanger. In thisstage, where a coolant cooler is concerned, the fluid is already cooledto a first temperature. In the second stage, which is illustrated by theparts 104 a, 110 b, 105 and 103 a, part of the fluid which, for example,has already been cooled in the first stage is cooled once again, so thatthis part of the fluid is cooled to a greater extent. The tubes arearranged, for example in the upper first region 110, 110 a, one behindthe other, as seen in the direction of flow of the second medium, sothat the tubes or fluid connections 110, 110 a are in each case arrangedin pairs and preferably on one plane. In this case, two or moreindividual tubes may be arranged one behind the other, or there may be asingle tube which has within its extent a multiplicity of fluid ductswhich are appropriately interconnected so that some of the ductsrepresent the fluid connection 110 and some of the ducts represent andform the fluid connection 110 a.

In the second region of the heat exchanger with the fluid connections 10b, individual tubes may also be used or a plurality of tubes, which areconnected in parallel with respect to the fluid flow, may be used foreach plane of the fluid connections. An individual tube or a pluralityof tubes may also be arranged as a fluid connection, these tubes atleast partially or also in each case again having individual fluidducts.

The number of fluid connections 110, 110 a belonging in each case to thefirst region and the number of fluid connections belonging to the secondregion may be designed according to size of the volume flow of the partvolume flows and to the corresponding target temperature of the fluid ofthe part volume flows. Preferably, the first region from the inlet 102to the first outlet 103 is the part region which has more fluidconnections than the second part region of the fluid connections 110 b.However, this may also be selected otherwise, depending on targettemperature and volume flow.

The division of the volume flows into the part volume flows takes place,inter alia, in the collecting chambers. These are separated from oneanother in the outer boxes 120, 121 of the heat exchanger by means ofwalls. The first outer box 120 is constructed in such a way that it hasa first partition 130 between the collecting chambers 104 and 104 awhich brings about fluidtight separation between these chambers.

The one chamber 104 is an inlet chamber which is delimited by the, forexample, box-shaped outer wall of the outer box and by the wall 130.Furthermore, the chamber 104 is delimited by the wall 130 which has afirst wall region 130 b, oriented perpendicularly to the planes of thefluid connections 110, 110 a, 110 b, and a second wall region, which isoriented essentially parallel to the respective planes of the fluidconnections 110, 110 a, 110 b.

The outer box 121 is separated inside it into two regions 104 b, 105 bythe partition 140, the partition 140 being oriented essentially parallelto the respective planes of the fluid connections. Thus, with the heatexchanger arranged vertically, the partition 140 is orientedhorizontally, according to FIG. 2.

In the exemplary embodiment of FIG. 2, the region 104 b serves as anintermediate chamber or deflecting or distributing chamber, the chamber104 serving as an inlet chamber, the chamber 105 as an outlet chamberand the chamber 104 a both as an outlet chamber and as an intermediate,distributing or deflecting chamber.

The outer or side boxes 120, 121 may preferably be produced from metalor plastic, in which case, in the plastic variant, the partitions 130,140 may be formed as parts produced in one piece with the box. The boxmay in this case be capable of being produced as a whole as an injectionmolding.

In FIG. 2, the tubes 110, 110 a, 110 b are arranged in such a way thatfree spaces 112 are provided as an air passage between them. Ribs 113are preferably arranged in at least some of these free spaces 112, inorder to form flow ducts for the air passage and to improve heatexchange between the air and the fluid passing through. The surface onthe cooling-air side is thereby increased as effectively as possible. Inthe case of a medium other than air, other ducts may also be provided,instead of an air passage.

The heat exchanger has the feature that the two participating media, forexample the cooling air and the fluid, are routed in crosscountercurrent in the first upper region of the fluid connections 110,110 a. In the lower region of the fluid connections, the twoparticipating media are arranged in cross current.

The tube sheets and water boxes or fluid box form chambers which serve,on the inlet side, for distributing the coolant stream or fluid streamto the tubes and, on the outlet side, for combining the coolant streamout of the tubes. The connections 102, 103, 103 a, such as, for example,connection pieces on the chambers, make it possible to connect the heatexchanger to a respective fluid circuit or part fluid circuit, such as,for example, a coolant circuit.

FIG. 1 illustrates the cooler network in a form of constructionpreferably consisting of flat tubes and corrugated ribs. The tubes mayhave the following forms of construction: round tube type ofconstruction, oval tube type of construction or bundle type ofconstruction.

The invention described here relates to fluid/fluid heat exchangers withcross current and/or cross countercurrent routing, to which one or morefluid streams are supplied at a high temperature level and from whichtwo or more fluid streams cooled to different temperatures emerge.

Both liquids, gases or liquid/gas mixtures may be considered as fluidaccording to the present application documents.

In the configuration according to the invention, the heat exchangerpreferably consists of a first single-row, double-row or multirowtube/rib system with distributing and collecting chambers, preferably atleast part of the heat exchanger having at least one deflection in depthwith cross countercurrent routing. A deflection essentially in a planeof the tubes or fluid ducts is to be understood as a deflection indepth. This deflection from the fluid connections 110 to the fluidconnections 110 a takes place in the chamber 104 b. A further part ofthe heat exchanger may also have the flow passing through it only onceor else in countercurrent, that is to say without or with deflection indepth.

In another exemplary embodiment, a deflection may also take place inwidth, the deflection in width being defined in such a way that thedeflection is oriented essentially perpendicularly to the planes of thefluid ducts.

Instead of the fluid connections or tubes arranged in two or more rows,a single-row arrangement of tubes may also be used, these tubes thenpreferably having in their core a separation of various fluid ductswhich correspondingly assume the function of the fluid connections shownin FIG. 2.

The tube/rib system may be a system with flat, oval or round tubes orelse be a system with other cross-sectional forms. The system may beassembled mechanically or soldered. The tube/sheet connection may bemade by mechanical forming, soldering, welding or adhesive bonding. Thetube/rib system and the distributing and collecting chambers may becomposed, for example, of the following materials, in particular ofaluminum, nonferrous metal, steel or plastic.

In the configuration according to the invention, the heat exchanger issubdivided into two or more regions by partitions in the collectingchambers, for example one region representing the cooler of a maincoolant circuit, and one or more further regions having the function oflow-temperature coolers or other coolers. The flow routing through theregions of the heat exchanger is determined by the partitions into thedistributing and collecting chambers and by connection pieces on thedistributing and collecting chambers. Each cooler region thus definedmay have intrinsically deflections in width or in depth.

These additional deflections are implemented by means of additionalpartitions in the distributing and collecting chambers.

To form the chambers, the partitions in the boxes are arranged ororiented straight, preferably horizontally or vertically, but, in otherexemplary embodiments, it may also be expedient if they have in sectionan l-shaped, z-shaped, T-shaped and/or U-shaped form or else anothercomposite form.

In a preferred refinement, a fluid, such as, for example, a coolant,enters a heat exchanger having two or more tube rows 110, 110 a throughonly one connection piece 102, specifically into the region whichconstitutes the cooler of the main coolant circuit. Furthermore, theheat exchanger has outlet connection pieces 103, 103 a, specifically ineach case one for the region of the cooler of the main coolant circuitand one for each low-temperature cooler region. This is associated witha cascading of the fluid stream, such as, for example, the coolantstream, that is to say, at each outlet connection piece, only part ofthe fluid stream or coolant stream emerging from the respective coolerregion is led out, the rest constituting the fluid stream or coolantstream entering the following cooler region.

The low-temperature regions in an integrated heat exchanger arepreferably arranged in such a way that regions through which coolant ofhigher temperature flows lie, in the cooling-air stream, behind or nextto regions through which coolant of lower temperature flows.

The fluid-side or coolant-side inlet cross sections in the regions areadvantageously, where appropriate, likewise stepped according to thecascading of the fluid stream or of the coolant stream. In this case,the stepping of the size of the inlet cross sections is to be selectedsuch that the flow velocity of the coolant, on the one hand, does notfall so sharply that the performance of the region is impaired and, onthe other hand, does not rise so sharply that the pressure loss becomesexcessively high. Preferably, the stepping of the size of the inletcross sections is selected such that the inlet cross section of thefollowing region of the heat exchanger or cooler region amounts tobetween ⅕ and ½ of the outlet cross section of the preceding region ofthe heat exchanger or cooler region. In further exemplary embodiments,the inlet cross section may amount even only to {fraction (1/10)} of theoutlet cross section of the preceding region or may even be equal to it.It is advantageous, moreover, if the stepping of the size of the inletcross sections is selected such that the flow velocity of the fluid orof the coolant is approximately equal in all regions. In particular, itis beneficial if the flow velocity of the coolant in a following coolerregion amounts to between 0.8 times and 1.2 times the flow velocity ofthe coolant in the preceding cooler region.

In the first preferred configuration, the flow routing of the coolantthrough the regions of the cooler is selected such that all theconnection pieces may be arranged as simple connection pieces arrangedon the cooler rear side. In a further exemplary embodiment of theinvention, at least individual connection pieces could be arranged as aninlet or outlet both on the cooler rear side or on the side or, ifappropriate, also on the cooler front side. The cooler rear side is inthis case defined as being the side which, with the cooler installed inthe vehicle, points in the direction of the engine space.

FIG. 3 shows once again an exemplary embodiment of a heat exchanger 200according to FIG. 2 in a diagrammatic illustration. The fluid or elsethe coolant enters the first region 202 of the cooler through the inlet201. The fluid flows from there through the fluid connections 203 intothe region 204. This region 204 is designed as a chamber and has adeflection in depth, that is to say essentially in the plane of thefluid connections. The fluid is led from the region 204 into the fluidconnections 205. The fluid flows from there into the chamber 206. Thischamber has, on the one hand, a deflection in width, since the fluid isled to the lower region of the chamber and is partially discharged therethrough the outlet 207 and, on the other hand, is partially routedthrough the fluid lines 208. The region 208 constitutes alow-temperature region without deflection in depth. The fluid flows fromthere in the region 209 and then through the outlet 210. As a result,the outlet connection piece of the first cooler region can be mounted onthe chamber on the cooler rear side at the point where the inlet intothe low-temperature region is located. The throughflow is cascaded, thatis to say part of the coolant emerges downstream of the first coolerregion and the other part enters the following low-temperature region.

FIG. 4 shows a heat exchanger in a diagrammatic illustration, parts ofthe heat exchanger 300 of FIG. 4 not being described again, insofar asthey are already illustrated in FIG. 2 or 3. The heat exchanger 300 has,in addition to the inlet connection piece 310 and the outlet connectionpieces 303 and 305, a further outlet connection piece 301. This givesrise to a further low-temperature region of the heat exchanger. Thislow-temperature region of the heat exchanger arises in the region 302,the region 304 constituting a further low-temperature region. The heatexchanger thus has three respective regions 302, 304 and 306 which areassigned in each case an outlet 301, 303 and 305, with only one inlet310. The flow passage through each of the three cooler regions issimple. A deflection in depth, preferably in the chamber 311, takesplace from the region 302 to the region 304. The intermediate walls 312,313 of the chambers are arranged, at 312, horizontally and, at 313, soas to be l-shaped in section, with a long leg in the vertical and ashort leg in the horizontal. As regards the partitions, however, othervariants may also be advantageous, depending on the configuration of thechambers of the side boxes.

FIG. 5 shows a heat exchanger 350 in a diagrammatic illustration, partsof the heat exchanger 350 of FIG. 5 not being described again, insofaras they are already illustrated in FIGS. 1 to 4. The heat exchanger 350of FIG. 5 has, in the first side box 360, a T-shaped intermediate wall351 consisting of a horizontal wall 351 b and of a vertical wall 351 awhich essentially stands on the horizontal wall. By virtue of thisconfiguration of the intermediate wall 351, the side box 360 is dividedinto three regions 361, 362, and 363, two regions on both sides of thewall 351 a and one below the wall 351 b.

The heat exchanger 350 has, in the second side box 390, an essentiallyz-shaped intermediate wall 392 consisting of a horizontal wall 392 a,and a vertical wall 392 b and a further horizontal wall 392 c. By virtueof this configuration of the intermediate wall 392, the side box 390 isdivided into two regions 391 and 393.

The region 361 is connected to the inlet 370. Starting from the region361, the fluid flows through the fluid connections of the region 380.The fluid flows from there into the region 393, is deflected there bothin depth and, if appropriate, in width and flows from there at leastpartially into the region 381. A further part flows out through theoutlet 395 a. The fluid stream which flows through the region 381 isdeflected in depth in the region 362 and then flows through the region382 back into the region 391. A further part of the fluid flows out ofthe region 391 from the outlet 395, and another part flows through theregion 383 after a deflection in depth in the region 391. The fluidflows from the region 383 into the region 363 and from there through theoutlet 395 b. The heat exchanger thus consists of a first cooler regionand of two further following coolers, a deflection in depth, that is tosay in the plane of the fluid connections, being present in the regionof the second cooler, and, furthermore, the latter also having adeflection in width. The regions 380, 381, 382 and 383 of the fluidconnections are arranged in such a way that the regions 381 and 382 arepreferably arranged in front of the region 230 in the air flowdirection, and the region 383 is arranged below these regions.

The heat exchanger 400 according to FIG. 6 constitutes a furtherembodiment, which differs from the variant according to FIG. 3 in thatthe low-temperature region is located partially in front of the firstcooler region with respect to the cooling-air stream. The intermediatewall 402 of the side box 401 is of z-shaped design, so that the fluidstream flows from the inlet 403 into the region 404. This region isformed, in the upper region, over the width of the side box and in thelower region has a restriction in extent due to division by the verticalintermediate wall. The fluid connections of the central region arelikewise divided into the regions 410 and 411 by means of a z-shapeddivision. The fluid, starting from the chamber 404, flows through theregion 410 into the side box 430, is partially deflected there in depthand in width and partially flows out through the outlet 431 and into theregion 411 and from there into the region of the side chamber 405 andfrom there through the outlet 432. Part of the region 411 of the secondcooler lies with its fluid connections in front of part of the cooler ofthe first region 410 in the direction of the air stream. The regions 410and 411 are of 1-shaped design in section.

FIG. 7 illustrates a design variant of a heat exchanger 450 which, ascompared with the heat exchanger of FIG. 6, has a horizontalintermediate wall 451 in the one side box and a further outlet 452 inthe region of the chamber 453. As a result, the fluid stream is bothdeflected from the region 460 into the region 461 and routed into theoutlet 452. The fluid then flows from the region 461 into the chamber ofthe side box according to FIG. 6. A deflection in width takes place,starting from the region 461, in the region of the side box. Thelow-temperature region of the heat exchanger of FIG. 6 is thus dividedinto two low-temperature regions by means of an additional partition andan additional connection piece. The region 460 is l-shaped in section.

FIG. 8 shows a further exemplary embodiment of a heat exchanger 500, theside boxes being interchanged in terms of the arrangement and form ofthe intermediate walls, as compared with FIG. 7, that is to say anintermediate wall 502 being arranged in a horizontal orientation in thefirst side box 501, and the side box 501 being divided into two regions,such as chambers, 503 and 504 which are arranged essentially one belowthe other. A z-shaped intermediate wall 521 is arranged in the secondside box 520 and divides the side box 520 into two regions 530 and 531which are essentially l-shaped in section.

The region 503 is connected as an upper chamber to the inlet 505. Thefluid flows from there through the fluid connection region 510 which isdesigned as an arrangement of fluid connections which is parallelepipedin section. The fluid flows from there in a deflection in width and indepth into the region 511 which is designed as an arrangement of fluidconnections which is parallelepiped in section. The fluid also flows outof the region 530 through the outlet 533. The fluid also flows throughthe region 511 and from there into the region of the chamber 504, wherea deflection in depth and, if appropriate, in width takes place, part ofthe fluid in the chamber 504 flowing out through the outlet 534 andflowing further on through the region 512 which is designed as anarrangement of fluid connections which is l-shaped in section. The fluidflows from there into the chamber 531 and from there through the outlet535. The heat exchanger of FIG. 8 constitutes a design variant whichdiffers from the heat exchanger according to FIG. 6 in that, by means ofa variation in the partitions and an additional connection piece, afurther low-temperature region is divided off from the first coolerregion.

FIG. 9 shows a design variant which differs from the heat exchanger ofFIG. 8 in that the second low-temperature region is divided into twolow-temperature regions by means of an additional horizontal partition550 and an additional connection piece 551.

The heat exchangers of FIGS. 2 to 8 have a cascaded throughflow and, atleast for a part stream, a deflection in depth.

FIG. 10 shows a section through a heat exchanger in the verticaldirection, for example vertically in relation to a plane of the fluidconnections. The tube/rib system 600 of the fluid connections is in thiscase designed, in the central region, at least in two rows with thefluid connection regions 601 and 602. This is expedient for thearrangement of the individual regions of the coolers, at least a partialdeflection in depth being provided.

The deflection may take place, for example, in the side boxes which arenot illustrated here. The deflection in depth is designed preferably incross countercurrent. The integrated heat exchanger is subdivided intofour regions 601, 602, 603 and 604, and each part region may have one ormore tube rows. Each part region may have a simple throughflow or adeflection in width or in depth. In some exemplary embodiments, the partregion 603 can be dispensed with. It is also possible to combine thepart regions 603 and 601 and the part regions 602 and 604 into oneregion in each case. The dimensions a, b and c transverse to thethroughflow direction of the integrated heat exchanger may be variedwithin defined limits. In this case, the sum a+b+c corresponds to theoverall dimension of the heat exchanger. A possible value of thedimensions a, b and c could be given, for example, by the insidediameter of the assigned connection piece or connection pieces. If thepart region 603 is omitted, a=0. The part region 604 is expedientlypresent and, if appropriate, without deflection in depth.

In a further preferred configuration of a heat exchanger, the flowrouting of the coolant through the regions of the cooler is selectedsuch that the large part of the connection pieces can be arranged assimple connection pieces arranged on the cooler rear side, whereas otherconnection pieces are arranged otherwise and, for example, are led outfrom the distributing and collecting chambers laterally or on the frontside. Different variants of this configuration are illustrated in FIGS.11 to 14.

The heat exchanger 700 of the exemplary embodiment of FIG. 11constitutes essentially a variant which differs from the heat exchangeraccording to FIG. 8 in that the two low-temperature regions 701 and 702are of equal size and, as a result, the second low-temperature region islocated not only partially, but entirely in front of the firstlow-temperature region. Furthermore, the wall 703 is of l-shaped designand divides the side box into two chambers or regions 704 and 705, theregion 705 lying at least partially in front of the region 704 in theair flow direction. Connected to the region 705 is an outlet 710 whichmay be directed toward the side or forward.

The heat exchanger 750 of the exemplary embodiment of FIG. 12constitutes essentially a further variant which differs from the heatexchanger according to FIG. 11 in that the main region 751 is largerthan the main region 711 and the one low-temperature region 752 issmaller than the low-temperature region 701. This is achieved in thatthe fluid connections are connected correspondingly and the wall 753 isof z-shaped design in section. The main region 751 thus lies partiallynext to or behind the region 754 and above the region 752, as seen inthe air flow direction. The two low-temperature regions 752 and 754 areof different size, and the second low-temperature region 754 is locatedpartially in front of the main region 751 and in front of thelow-temperature region 752.

The heat exchanger 800 of the exemplary embodiment of FIG. 13constitutes essentially a further variant which differs from the heatexchanger according to FIG. 12 in that the one low-temperature region801 is larger than the low-temperature region 752, and thelow-temperature region 802 is smaller than the low-temperature region754. This is achieved in that the fluid connections are interconnectedcorrespondingly and the wall 810 is of c-shaped design and is formedessentially from two horizontal walls with one vertical wall. The mainregion 804 thus lies partially behind the region 802 and above theregions 802 and 801, as seen in the air flow direction. Thelow-temperature region 802 lies above the region 801. The region 802 isthus arranged between the region 801 and 804, the region 801 beingpartially directly adjacent to the region 804. The two low-temperatureregions 801 and 802 are of different size. The heat exchanger 800 ofFIG. 13 constitutes a variant of the heat exchanger of FIG. 7 whichdiffers from the latter in that the sequence of throughflow of the twolow-temperature regions 801, 802 is interchanged. This means that,starting from the inlet connection piece 811, the flow passes firstthrough the region 804, then through the region 801 and subsequentlythrough the region 802, a corresponding deflection of the fluid streamtaking place in the chambers 812 and 813.

The heat exchanger 850 of the exemplary embodiment of FIG. 14constitutes essentially a further variant which differs from the heatexchanger according to FIG. 12 in that the one low-temperature region754 is divided as a result of a further division into twolow-temperature regions 851, 852, so that, overall, there are threelow-temperature regions 851, 852, 853.

This is achieved in that the fluid connections are interconnectedcorrespondingly and the wall 860 is of h-shaped design and is formedessentially from two horizontal walls with one vertical wall, the lowerhorizontal wall extending over the width of the side box and the upperhorizontal wall extending only over a part region of the width of theside box. The main region 854 thus lies partially behind the region 851and above the regions 852 and 853, as seen in the air flow direction.The low-temperature region 851 lies above the region 852. The region 853is arranged in front of the region 852 in the air flow direction.

The illustration of FIG. 15 shows a section through a heat exchanger 880in the vertical direction. The tube/rib system is at least partially ofat least two rows, an at least partial deflection in depth beingprovided. The deflection in depth may in this case be designed in crosscountercurrent.

The integrated heat exchanger is subdivided into regions 881, 882, 883,884 and 885 of fluid connections, and each part region may have one ormore tube rows. Each part region may have a simple throughflow or adeflection in width and/or in depth. Optionally, for example, the partregion 884 and/or 885 could be dispensed with. It is also possible tocombine the part regions 881 and 882 and the part regions 883 and 885into one region in each case. The dimensions a, b and c transverse tothe throughflow direction 890 of the integrated heat exchanger may bevaried according to the invention. In this case, the sum a+b+c isadvantageously the overall dimension of the heat exchanger. A minimum ofeach of the dimensions a, b and c is given, where appropriate, by aninside diameter of the assigned connection piece or connection pieces.If the part regions 884 and 885 are omitted, c=0. The part region 881 ispreferably present and, if appropriate, with/without deflection indepth.

FIG. 16 shows a heat exchanger 900 which is equipped with a tube/ribsystem by means of a central region 901 which is divided into differentregions. Furthermore, the heat exchanger has laterally arranged sideboxes 902 and 903, the side boxes being subdivided into individualchambers as a result of the arrangement of intermediate walls. Some ofthe chambers are in this case connected to at least one inlet and/or atleast one outlet.

The central region 901 is subdivided into five separate regions of fluidconnections, the regions, in each case considered separately, havingparallel-connected fluid connections which are not connected to fluidconnections of the other regions within the regions. As seen in the airflow direction, two regions 910, 911 are arranged at the upper end ofthe heat exchanger 900, the region 910 being arranged in front of theregion 911 in the air flow direction. The two regions, while havingessentially the same extent in depth, share the construction depth ofthe heat exchanger. In this respect, there may also be different extentsin depth and, if appropriate, also in width. Below these two regions isarranged a third region 912 which extends over the entire depth of theheat exchanger. Below this region, two further regions 913, 914 arearranged at the lower end of the heat exchanger 900, as seen in the airflow direction, the region 913 being arranged in front of the region 914in the air flow direction. The two regions, while having essentially thesame extent in width, share the construction depth of the heatexchanger. In this respect, there may also be different extents in depthand, if appropriate, also in width.

The fluid flows through the inlet 920 through the connection piece intothe chamber 921 which is formed in the side box by the wall 922 and bythe wall of the side box. The fluid subsequently flows through theregion 911 and is deflected at least partially in depth in the chamber930. The chamber 930 is formed by the wall of the side box 903 and bythe intermediate wall 931. Furthermore, part of the fluid flows outthrough the outlet 940. The fluid which is deflected in the chamber 930subsequently flows back through the region 910 and enters the chamber923 which is formed by the wall 922 and by the horizontal wall 924 inthe side box 902. In the region of the chamber 923, the fluid ispartially deflected in width, so that it flows into the region 912, andanother part of the fluid emerges at the outlet 940.

The fluid which flows through the region 912 passes from there into thechamber 932, is partially deflected again there and flows partially intothe region 914. Another part can flow out through the outlet 941. Thefluid which flows through the region 914 enters the chamber 925 which isformed by the wall of the side box and by the horizontal intermediatewall. In this chamber, the fluid is partially deflected in depth and thefluid partially flows through the outlet 942. The defected fluid thenflows through the region 913 and passes from there into the chamber 933where it flows out through the outlet 943. The heat exchanger thus hasone inlet and four outlets. This results, overall, in an integrated heatexchanger in which a large part of the connection pieces could bearranged on the cooler rear side, while other connection pieces are ormay be arranged otherwise and, for example, are led out of thedistributing and collecting chambers laterally or from the front. Inthis configuration, a plurality of part regions can be produced, whichmay in each case have one or more tube rows. Each part region may have asimple throughflow or a deflection in width and/or in depth.

In a further preferred configuration, the heat exchanger has more thanone inlet. A “cascaded” throughflow of all the cooler regions suppliedwith coolant from a single inlet connection piece is therefore replacedby the mutually independent coolant supply of individual part regions orgroups of part regions. This configuration can be produced from all theconfigurations and variants described above by means of additionalpartitions and connection pieces.

FIG. 17 shows a further diagrammatic illustration of a heat exchanger1000, in which two inlets are provided and, furthermore, three outlets.FIG. 17 shows a heat exchanger 1000 which is equipped with a tube/ribsystem by means of a central region 1001 divided into different regions.Furthermore, the heat exchanger has laterally arranged side boxes 1002and 1003, the side boxes being subdivided into individual chambers as aresult of the arrangement of intermediate walls. Some of the chambersare in this case connected to at least one inlet and/or at least oneoutlet.

The central region 1001 is subdivided into three separate regions offluid connections, the regions, in each case taken separately, havingparallel-connected fluid connections which are not connected to fluidconnections of the other regions within the regions. Two regions 1010,1011 are arranged at the upper end of the heat exchanger 1000, as seenin the air flow direction 1099, the region 1010 being arranged in frontof the region 1011 in the air flow direction. The two regions, whilehaving essentially the same extent in width, share the constructiondepth of the heat exchanger. In this respect, there may also bedifferent extents in depth and, if appropriate, also in width. Belowthese two regions is arranged a third region 1012 which extends over theentire depth of the heat exchanger.

The fluid flows through the inlet 1020 through the connection piece intothe chamber 1021 which is formed in the side box by the wall 1022 and bythe wall of the side box. The fluid subsequently flows through theregion 1010 and is deflected at least partially in depth in the chamber1030. The chamber 1030 is formed by the wall of the side box 1003 and bythe intermediate wall 1031. Furthermore, part of the fluid flows outthrough the outlet 1040. Further fluid flows through a further inlet1041 into the chamber 1030. The fluid which is deflected in the chamber1030 or which flows into the chamber through the further inletsubsequently flows back through the region 1011 and enters the chamber1023 which is formed by the wall 1022 and by the wall of the side box1002. In the region of the chamber 1023, the fluid is partiallydeflected in width, so that it flows into the region 1012, and anotherpart of the fluid emerges at the outlet 1042.

The fluid which flows through the region 1012 passes from there into thechamber 1032 and flows from there out through the outlet 941. The heatexchanger thus has two inlets and three outlets.

In a further preferred refinement of the invention according to FIG. 18,the heat exchanger 1100 has, for example, a single-row tube/rib system1101 and two side boxes 1102 and 1103. This heat exchanger is precededby a further heat exchanger 1199 in the cooling-air stream 1198. Theheat exchanger may also be formed from only one tube row or from aplurality of tube rows for which no deflection in depth is provided. Inthis case, however, deflections in width may be provided, or the partregions of an integrated exchanger lie next to one another.

The configuration principles described above may be applied, in thiscase too, when the integrated heat exchanger is preceded by at least onefurther heat exchanger in the cooling-air stream and these areconnected, for example, to form a module. This preceding heat exchangeror these preceding heat exchangers are advantageously positioned withrespect to the individual regions of the integrated heat exchanger insuch a way that the flow routing and temperature level in the precedingheat exchangers corresponds approximately to the situation in the “fronthalf” of an integrated heat exchanger according to the configurationprinciples of the figures described above.

According to the invention, it may be expedient if, in heat exchangers,the connection pieces for the inlet and/or outlet are not only led outon the cooler rear side or laterally, but, where appropriate, also atthe top and bottom or on the cooler front side, as seen in the air flowdirection. The connection pieces may in this case be attached or bedesigned as angle connection pieces or connection pieces led through.

The configuration features of the heat exchangers can not only beapplied to the crosscurrent cooler described, but also to downflow orupflow coolers.

The configuration features are also reversible in terms of right/leftand top/bottom.

The integration of a plurality of heat exchangers into one structuralunit saves, in particular, construction space for the cooling module.Whereas individual heat exchangers would have to be at minimum distancesfrom one another in the cooling module, the heat exchanger regions in astructural unit directly adjoin one another. Specific parts may alsoassume a double function since, as intermediate elements, they canassume functions for a plurality of heat exchanger regions.

A deflection in depth and/or the arrangement of cooler regions with alow temperature level in the cooling-air stream in front of coolerregions with a high temperature level advantageously improve theeffectiveness of the heat exchanger.

The cascading of the coolant stream over a plurality of cooler regionsexpediently reduces the number of connection pieces required andconsequently the number of interfaces. The number of hoses and hoseconnections required and the coolant content are consequently alsoreduced.

The stepping of the inlet cross sections of the cooler regionsadvantageously makes it possible to maintain favorable conditions forheat transmission and pressure drop across all the cooler regions.

Large low-temperature regions which may comprise a plurality oflow-temperature coolers are advantageously possible.

The low-temperature regions with a cascaded throughflow may in each casedeliver cooling power for the assembly assigned to them and additionallyfor further assemblies. In this context, “cascaded” means that in eachcase parts of a fluid stream are branched off in stages or steps and theremainder of the fluid flows further on through the heat exchanger. Thefluid quantity flowing further on through the heat exchanger is in thiscase additionally cooled, so that fluid quantities or mass flows with adifferent temperature are available at various outlets of the heatexchanger. The respective quantities of the fluid at a given temperaturecan be controlled accurately by means of the design of the respectiveregions of the heat exchanger.

Preferably, the regions of the heat exchanger which generate fluid witha lower temperature are preferably arranged in front of or next to otherregions with respect to the cooling-air stream or another cooling massflow.

FIG. 19 shows the diagrammatic illustration of a cooling circuit with aheat exchanger 1201, a condenser 1202 and assemblies, such as, forexample, an engine 1203, a starter generator 1204, a transmission withtransmission oil cooler 1206, a cooler for electronics 1207 of thevehicle, a charge air/coolant cooler 1208, a pump 1209, a thermostaticbypass valve 1210 and a multiplicity of lines.

The condenser 1202 may be arranged as an independent component or bedesigned as a structural unit with the heat exchanger or be integratedwith the heat exchanger 1201.

The diagrammatic figure shows by way of example a heat exchanger 1201according to an illustration of FIG. 17. The heat exchanger 1201 has aninlet 1220, through which a fluid, such as coolant, flows out of theline 1221 into the heat exchanger. The fluid then flows through thefluid connections, for example a tube/rib system, and flows out againpartially at the respective outlets 1222, 1223, 1224. The temperaturesof the respective coolant stream at the respective outlets are differentand, depending on the design, may differ by between approximately 10degrees Celsius and 40 degrees Celsius or more. In the present example,the temperature at the inlet is approximately 115 degrees Celsius, atthe outlet 1222 approximately 110 degrees, at the outlet 1224approximately 80 degrees and at the outlet 1223 approximately 60degrees. However, these values depend on the respective configuration ofthe heat exchanger and of the circuit.

The fluid with the highest temperature flows from the outlet 1222 to thecoolant inlet of the engine 1203 via the pump 1209. It is heated there,and the heated fluid flows from the coolant outlet of the engine 1203through the line 1221 to the heat exchanger inlet 1220. Arranged betweenthe line 1230 and the line 1221 is a thermostatic bypass valve which,according to predetermined characteristic values, at least partiallyopens or closes the bypass connection, so that the engine can heat upmore quickly, for example in a cold start situation, than when the fluiddoes not run or does not run completely through the cooler.

Connected to the outlet 1224 is a further line 1231 connected to an oilcooler in which heat exchange between the fluid and the transmission oiltakes place. The fluid heated in the oil cooler 1206 flows through theline 1232 and enters the line 1230.

Connected to the outlet 1223 is a further line 1233 which is connectedto a cooler 1207 for electronics and consequently in series with acharge air/coolant cooler 1208. The fluid heated in this way flowsthrough the line 1234 and enters the line 1230 and, after flowingthrough the engine, passes into the heat exchanger 1201 again.

It is particularly advantageous that only one pump 1209 is used in thisarrangement of a main cooling circuit and of secondary cooling circuits.This is achieved in that the returns of the secondary circuits issue inthe main circuit upstream of the pump, that is to say are connected tothe suction side of the pump or the low-pressure side of the pump. Thesecondary cooling circuits are led parallel to the bypass valve 1210.

This pump may be a pump driven by an electric motor or a pump driven bythe engine 1203, in which case the pump driven by the electric motor canpreferably be operated according to the cooling requirements, that is tosay also in the electrically or electronically regulated mode.

The arrangement of a pump for supplying a main cooling circuit and atleast one secondary cooling circuit may advantageously be provided,since the at least one secondary circuit is led parallel to the bypassvalve 1210.

1. A heat exchanger, in particular for motor vehicle cooling systems,with at least one fluid inlet and at least two fluid outlets, and withan arrangement of fluid connections between inlet, collecting,deflecting and/or outlet chambers, the fluid connections beingsubdivided into various regions, a first region of fluid connectionsbeing arranged between at least one inlet and one first outlet, and afurther region of fluid connections being arranged between the firstoutlet and a second outlet.
 2. The heat exchanger as claimed in claim 1,characterized in that a further third outlet is arranged and a furtherregion of fluid connections is provided between the second outlet andthe third outlet.
 3. The heat exchanger as claimed in claim 1,characterized in that a further nth outlet is arranged and a furtherregion of fluid connections is provided between the n−1-th outlet andthe nth outlet, n preferably being 3, 4, 5, 6, 7, 8, 9, 10 or greaterthan
 10. 4. The heat exchanger as claimed in claim 1, characterized inthat individual regions of fluid connections are connected to otherregions of fluid connections and/or to an inlet and/or an outlet bymeans of inlet, collecting, deflecting and/or outlet chambers.
 5. Theheat exchanger as claimed in claim 4, characterized in that the inlet,collecting, deflecting and/or outlet chambers are arranged preferably inside boxes arranged laterally with respect to the fluid connections, theside boxes being capable of being subdivided into various chambers bymeans of partitions.
 6. The heat exchanger as claimed in claim 5,characterized in that the partitions are designed as vertical,horizontal or l-shaped, z-shaped, c-shaped or t-shaped walls or as wallsformed compositely from these.
 7. The heat exchanger as claimed in claim1, characterized in that a deflection in depth, that is to say in aplane of the fluid connections, is present between at least one firstregion of fluid connections and one second region of fluid connections.8. The heat exchanger as claimed in claim 1, characterized in that adeflection in width, that is to say in a plane perpendicular to a planeof the fluid connections, is present between at least one first regionof fluid connections and one second region of fluid connections.
 9. Theheat exchanger as claimed in claim 1, characterized in that a deflectionin depth and in width, that is to say in a plane of the fluidconnections and in a plane perpendicular to a plane of the fluidconnections, is present between at least one first region of fluidconnections and one second region of fluid connections.
 10. The heatexchanger as claimed in claim 1, characterized in that two regions offluid connections are routed in countercurrent without an outlet betweenthem.
 11. The heat exchanger as claimed in claim 1, characterized inthat ducts for a further medium or fluid are provided between the fluidconnections.
 12. The heat exchanger as claimed in claim 11,characterized in that these ducts are formed by ribs between the fluidconnections.
 13. The heat exchanger as claimed in claim 11,characterized in that the medium is air.
 14. The heat exchanger asclaimed in claim 11, characterized in that the medium is a fluid orliquid medium.
 15. The heat exchanger as claimed in claim 1,characterized in that the fluid connections are tubes, preferably suchas flat tubes or round tubes or oval tubes.
 16. The heat exchanger asclaimed in claim 1, characterized in that the tubes have a plurality offluid ducts which do not communicate with one another over the length ofthe tubes.
 17. The heat exchanger as claimed in claim 1, characterizedin that the fluid connections or tubes have a plurality of fluid ductswhich communicate with one another over the length of the tubes.
 18. Theheat exchanger as claimed in claim 1, characterized in that the fluidconnections or tubes are arranged in a single row or in a plurality ofrows next to one another for each plane of the fluid connections.
 19. Afluid circuit with at least one heat exchanger having at least one inletand at least two outlets and with at least two assemblies which can besupplied by the heat exchanger by means of fluid lines and have a fluidinlet and a fluid outlet, characterized in that a pump with an inlet andoutlet is arranged between one outlet of the at least one heat exchangerand one inlet of at least one assembly, and at least one outlet of afurther assembly can be connected to the inlet side of the pump.
 20. Thefluid circuit as claimed in claim 19, characterized in that the furtherassembly is connected with its inlet to an outlet of the heat exchanger.21. The fluid circuit as claimed in claim 19, characterized in that aplurality of further assemblies are connected in series and have a fluidflowing through them.
 22. The fluid circuit as claimed in claim 19,characterized in that a plurality of further assemblies are connected inparallel and have a fluid flowing through them.
 23. The fluid circuit asclaimed in claim 19, characterized in that the inlet of a furtherassembly is connected to an outlet of the heat exchanger.